High speed punch press



May 4, 1943. ca. B. SCHEFFEY HIGH SPEED mmcn PRESS Filed March 25, 1941eat 1 6 Sheets-Sh May 4, 1943. s. B. SCHEFFEY HIGH SPEED PUNCH PRESSFiled March 25 1941 6 Sheets-Sheet 2 May 4,1943. 6. B. SCHEFFEY HIGHSPEED PUNCH PRESS Filed March 25, 1941 s Sheets- Sheet s May 4, 1943-(5. B. SCHEFFEY HIGH SPEED :uucn PRESS I 6 Sheets-Sheet 4 Filed March25, 1941 M 4, 1943- G. E. S CHEFFE'Y 2,318,107

HIGH SPEED PUNCH PRE-SS Filed March 25, 1941 e Sheets-Sheet 5 May 4,1943, I e. B. SCHEFFEY Patented May 4, 1943 UNEE ST TES ATENT F F l C EHIGH SPEED PUNCH PRESS George B. Schefiey, Reading, Pa., as'signor'toJames H. Sternbergh, Reading, Pa., and himself, jointly 30 Claims.

This invention relates to high-speed machines and more particularly topunch or die presses for working on sheet strip or coiled metal. Theterm high speed as herein used is to be interpreted as relating to thespeed at which the punch or tool actually penetrates the metal andperforms the punching operation rather than the number of blanks, forexample, which may be delivered per minute.

The primary purpose of the invention is to efi'ect an increased rate ofproduction with the exceptional extension of the life of tools and diesand an improved quality of work with an expenditure of notably lesspower and with greater flexibility and variety of performance than ispossible with present machines. And it is with respect to such machinesthat the invention will be hereinafter described.

One of the objects of the present invention is to provide a strong andsubstantial machine which will easily and rapidly perform the Workintended upon metal stock in strip or coil form either as a series ofcontinuously repeating operations or as single operations, as desired.

A further object is to provide a practical machine of the abovecharacter which willhave an extremely high operating speed and a stillhigher punch action thereby to reduce the wear upon the die and punch. I

A further object is to provide a substantial automatic machine of theabove character in which the actual punching operation is accomplishedby a substantially instantaneous blow as distinguished from the nowcommon relatively lowspeed, high-pressure punching operations of otherpresses. I

A further object is to provide a press of the last above-mentionedcharacter in which the punch may operate against the metal substantiallywithout entering the die at any time.

A further object is to provide a machine of the above character withimproved lubricating means.

A further object is to provide a machine which may be easily and quicklyset up according to the variations in material operated upon and toolsemployed Within a minimum time and with absolute assurance of accuracyof position.

A further object is to provide an improved machine of the abovecharacter which may be easily and quickly converted to and from singlepress operations or multiple series operations as desired.

A further object is to provide a practical press which will be reliableand safe in useand operation and which will be substantially automaticin its performance.

A further object is to provide a press of the above character which maybe started and stopped by suitable conveniently positioned actuatingmembers thereby increasing the safety to th operators. I

A further object is to provide a high-speed punch press which may beeasily and quickly converted from one style of Work to another as far aschanging of punches or dies is concerned and after such changes may beeasily and quickly adjusted with respect to the thickness of the Workand the relative position of the die bed with respect to the cooperatingtools.

Other objects will be in part obvious from the annexed drawings and inpart hereinafter indicated inconnection therewith by the followinganalysis of this invention.

This invention accordingly consists in the features of construction,combination of parts, unique relation of members, and the relativeproportioning and disposition thereof, all as more completely outlinedherein.

To enable others skilled in the art fully 'tocomprehend the underlyingfeatures of this invention, that they may embody the same by thenumerous modifications in structure and relation contemplated by theinvention, drawings depicting two embodiments of the invention form apart of this disclosure, and in such drawings like characters ofreference denote corresponding parts throughout the several views, inwhich- Figure 1 is a front elevational view of the upper part of thecomplete machine.

Figure 1a. is a similar view of the lower part.

Figure 2 is a side elevational view of the same machine showing theupper part disclosed in Figure 1.

Figure 2a is a similar view taken at right angles to Figure 1a andtogether show the complete machine.

Figure 3 is an enlarged detailed view showing the feed rollers, certainparts being in cross-sec.- tion.

Figure 4 is a detailed perspective viewof one set of feed rollers.

Figures 5 and 6 are detailed sectional views with the set of feedrollers in different positions.

Figure 7 is'a detailed View of the" wiring diapact member shown inFigure 1.

In order that a clearer perception of the pres' ent invention may be hadit is to be noted that the present machine comprehends an unusuallyhigh-speed mechanism, that is, one in which the main operating shaft mayefficiently turn at approximately 1000 R. P. M. with a 1" stroke orapproximately 2000 R. P. M. with stroke and consequently produce acorresponding number of punchings or like operations. It is to beunderstood that the terms punch or punching are to be used in a broadsense, that is, denoting a tool and either an actual piercing orpunching operation or a series of punches or dies operatingsimultaneously but in sequence upon a strip of metal as fed, forexample, to provide a finished article of the desired size and shape.When used with a series of tools it is customary to include the usualpunch and pilot which are here omitted for the sake of clearness.

Referring now in detail to the drawings, and more particularly toFigures 1, 1a, 2 and 2a, the entire press mechanism is for the most partenclosed in a suitable rectangular or box-like casing mounted upon alarge and substantial base 2| which may be secured to a factory floor orthe like in any desired manner. Outside of the base 2| and casing 20 asuitable source of power is provided such as an electric motor 22together with transformer, speed control, etc. (not shown). These partsform no part of the present invention except insofar as they may enterinto certain combinations hereinafter set forth, and

are of standard construction and need no detailed explanation orillustration.

A main power shaft 23 extends fore and aft of the casing 20 through theupper part and is driven directly and independently from the motor 22modate the machine to variations in weight of V the punches and diesemployed. Such means which may be a plate 21 or the like, also are ofwell known construction and further details thereof are unnecessary.

These above mentioned parts broadly indicated in Figures 2 and 2a,include the motor 22 and its V-belt 24, to drive the power shaft 23extending forwardly through the machine, the clutch 25, thecounterbalancing flywheel 26 and a suitable crosshead mechanism, asshown in Figure 1, to a front bearing 28. It is the peculiarconstruction and novel arrangement of the parts of this'crosshead whichcontribute largely to make effective the high speed of the entiremachine.

As shown more clearly in Figure 1 the crosshead comprises vertical sideguides 30, secured in any desired manner to the inner walls of thecasing 20. These guides are preferably V-shaped in cross-section, asshown more clearly in Figure 10, and accommodate the vertically slidingportion 3| of the crosshead. This vertically sliding member 3| isgenerally rectangular in shape and is provided with correspondingbuilt-up, V- shaped gibs 32, of hardened steel, sliding in the bronzegrooves 30, at the sides of the casing.

The horizontal top and bottom portions, 33 and 3d, of the verticallymoving crosshead member are provided with horizontal V-grooves spacedapart, vertically, one from the other, as clearly 7 shown in Figure 1,thereby to accommodate the horizontally sliding portion 35 of thecrosshead which is also provided with similar V-shaped gibs 35 coactingwith these upper and lower grooves 33 and 34 in the vertically slidingmember 3 l.

The main driving shaft 23 passes through the horizontally slidingcrosshead part 35 and is provided with suitable means such as a crank oreccentric 31, turning in antifriction bearing 40, of any suitable style,the outer periphery of which bearing is mounted in the horizontallysliding member or part 35. The lower portion of the horizontally slidingmember is provided with a reinforcing hardened steel striking member orhammer 4| the lower portion of which is slightly wedge-shaped, as shownin Figure 9, thereby to cooperate with a similarly shaped upper portion42 of the punch or die actuating hammer 43.

From the above it will be seen that as the main power or driving crankshaft 23 turns in its fore and aft bearings 44 and 45, under the actionof the motor, the eccentric 31 turns withinthe roller bearing cage 40and performs two functions. First, it moves the vertically slidingportion 3| of the crosshead in a straight up-and-down direction, as mustnecessarily follow by reason of the location, construction and positionof the guides 30 on the inside of the casing frame 20, andthe movementof this vertically reciprocating portion of the crosshead has thewell-known sine curve action, that is, maximum speed intermediatebetween accelerating and decelerating speeds and stops at the top andbottom of its stroke. Second, the horizontally sliding member 35 is alsoreciprocated relative to the vertically sliding portion 3| of thecrosshead and this, its relative movement, is also confined to astraight line, from one side to the other of the vertically moving part3|, under the action of the guides 33 and 34 in the vertically movingcrosshead member 3| and its relative rate of movement also follows asine curve but is degrees out of phase with that of the verticallymoving part 3|. In other words, the horizontal movement accelerates anddecelerates from and to complete stops at the ends of its horizontalreciprocation, when the part 3| moves fastest, but travels with maximumspeed at the center of its stroke when part 3| is stopped at the ends ofits stroke. While the member 35 travels horizontally with respect topart 3| it nevertheless has an actual circular movement, as it iscarried by the eccentric 31 of the driving shaft 23. Thus the hammer 4|and the top or anvil of the punch 43 come into engagement just beforethe point of zero speed of the down stroke of the vertically movingmember 3| and just as the horizontal member 35 is attaining its maximumspeed. So the hammer 4| of the crosshead hits the anvil 42, Fig. 9, ofthe punch a quick, powerful, glancing blow while traveling atsubstantiallymaximum. horizontal speed and while the vertically movingcrosshead 3| is substantially resting at the end of its down stroke andpressing the punch against the work. Thus the hammer blow adds a swiftimpact to the relatively slow crosshead pressure and all the movingparts cooperate, in acting upon the punch with the result that the punchis driven quickly and powerfully through its short, quick working strokethereby effectively performing the desired action with little if anyactual movement of the tool or punch 50 into the die As actualpenetration of the punch into the die can be greatly reduced or entirelyomitted, the wear life of the punch and die are very materiallyincreased. The machine may be speeded up far beyond ordinaryexpectations because the motion of the inner crosshead 35 is timed andbalanced with crosshead 3| and the adjustable balance wheel 26 isprovided to compensate for different weight punches.

The more nearly the two main parts of the cross head 31 and 35 equaleach other in weight the better the balancing effect obtained, togetherwith a greater decrease in vibration when the machine is in operation.

Work feed With a punch operating mechanism such as above set forth it isof course necessary to provide means for feeding the work strip 52relative to the punch 59 with proper timing and sequence to permit thedesired result to be accomplished. There is therefore provided a mainset of feed rollers shown at the right of Figure 1 and in detail inFigures 3 to 6 lying substantially immediately above and below thehorizontal plane of the die 5| and to one side thereof and controlled inits operation largely by a solenoid 80. It is also desirable to providea corresponding set of feed rollers at the opposite side (left ofFigure 1) of the die 5! to receive the work strip 52 as it is fedbetween the punch and die 5! and, particularly, to eject the final endof the work strip after the first set of feed rollers has ceased tocontact and function thereupon.

The feed rollers at the right of the machine, as I shown in Figure 4,comprehend an upper and a lower roller, 53 and 54, shown in sectionaldetail in Figure 3. The surfaces of these rollers are segmented (seeFigures 5 and 6) in such a manner as to engage the work strip with afeeding action through a portion of their rotation only and at othertimes to leave the feed strip unengaged, during the actual punchingoperation. The relative length of the effective feeding segments can beeasily and quickly adjusted by the mechanism shown in Figure 3, as willbe more fully hereinafter described.

It is also necessary that the feeding operation of these feed rollers besynchronized with the reciprocation of the crosshead and that they movethe work strip into the proper position to be worked upon by the punch,well before the crosshead reaches its lowermost position. The feedingmay be done at any time when the solenoid 80 is not holding the rollersin operating position, even tho the machine is running. It is a featureof this press that feeding may be done early or late.

Referring again to Figure l, the work strip 52 while being punched,passes between the two feed rollers 53 and 56; thence towards the leftover the die 5| supported on a die bolster 55, to the opposite side ofthe machine where it passes between feed rollers and 51. However, beforethe work strip '52 can be properly fed to the punch 55 it must first beinserted between the feed rollers and have its feed end contact a stopmember 60 which is adjustable with relation to the punch and dieposition. When the machine is at rest the stop 60 has a position abovethat disclosed in the lower part of Figure 1, and with the part 60 inthe normal horizontal path of travel of the work strip. Thus, with thework strip in this position, the rollers. 5354 are normally out ofengagement, the upper roller being free to slide in vertical bearings6|, under the action of coacting cam members 62 and 63, in the frame 64,which are brought into engagement by a relative sliding movement of arod 65 acting against a compression spring 66 and under the action of alaterally movable and upwardly extending arm 61 of a bellcrank m. Thisbellcrank is pivoted at I j, at the right side of the roller bearingframe 64, while the opposite bellcrank arm 12 extends laterally tosupport, by links l3, a transverse rod or shaft 14 more clearly shown inFigure 4. The central part of this shaft is connected by means of aturnbuckle link 15 adjustably secured at its lower end to a laterallyextending arm 15 pivotally mounted at 17, Figure 2a. The opposite end ofthis arm is moved by the action of the solenoid 80. Thus when thesolenoid 8B is energized it exerts a downward pull through lever 76 andlinks 15 on the arm 12 and causes a corresponding turning of thebellcrank lever 10 and a lateral movement of the rod 65 towards theright thereby causing the engaging cams 62 and 63 to move the upper feedroller 53 downwardly into engagement with the lower feed roll 5d the topof which is level with the die 5 5.

Feed brake mechanism Before taking up the circuits and mechanismsactuating the solenoid, reference is again mad to Figure 1 showing abrake acting upon the work stock 52 for stopping the movement of thestock at the desired moment relative to the actuation of the crossheadand punch 55). Obviously this brake release must also be operated insynchronism with the up and down movement of the crosshead. There is,therefore, provided upon the horizontal member of the crosshead a rollerbearing cage 8! suitably mounted upon a stud S2 and which cage isprovided with an outer or surrounding member provided with a laterallyextending arm 83 which telescopes within a recessed sleeve 84 theopposite end of which sleeve is provided with a pin 85 passing through ahole in a stud 88 adjustably mounted in one of several holes Bl upon theupper end of the vertical arm 953 of a bellcrank lever pivoted at 9|.Thus it will be seen that the horizontal crosshead member 35 is free tomove up and down and laterally under the action of its driving eccentric23 and at the same time maintain mechanical connection with the stud 86on the bellcrank arm $51 and cause the arm to rock back and forth insynchronism with the reciprocations of the crosshead.

This bellcrank lever pivotally mounted upon a pin 91 in the side wall ofthe casing 2i] has its horizontal arm 92 extending outwardly through theside of the casing to connect loosely with the upper end of a spacer rodor link 93, the lower end of which link has loosely and adjustablysecured thereto a laterally extending arm 94 of a bellcrank leverpivoted at 95, th lower nd or arm 94 of which constitutes a brakeadapted to engage horizontally across the work strip 52 and press itagainst part 96 as clearly. shown in Figure 1. Now as the crossheadmoves up and down the bellcrank levers 90 and 94' are rocked about theirpivots to cause the brake 94'9B to alternately brake and drag upon thetop surface of work strip to stop and again permit it to be movd, as bya pilot, and fed by the feed rolls. Such variations in engagement, ofcourse, must take place in proper timing with the reciprocations of thepunch 50. After the work strip has been stopped, part 96 relaxes itspressure and acts as a friction drag while punch 50' does its work.

On the side frame of the machine is a laterally extended support 97 forholding a slidingly adjustable member I00, as shown more clearly inFigure 1, thereby to permit the effective braking surface or distancebetween 94 and 96 to be adjusted according to the thickness of the workstock and die height. Suitable adjusting nuts I M are provided betweenthe supports 91 for the bellcrank lever and the slide I whereby theparts may be securely locked in adjusted position.

Stop release As shown in Figure 1 and detailed in Figure 12, mountedupon the inner side of one of theouter end frame plates I02 for the feedrollers 5354 is a lever I03 pivoted at I04, the upper end of which leveris adapted to be engaged by an adjustable stud I depending from member55, Fig. 4 while the lower end coacts with a pin I06 mounted upon agenerally square or rectangular member I0'I mounted upon a transverseshaft I08. (Figure 1). This rectangular or square member I01 carries thefeed stop.60 previously mentioned and by rotating the entire member I01about its axis this stop member 60 is brought into and out of the pathof travel of the work strip 52,

shown in out position in Figure 1. lDiagonally opposite the stop lip 60there is provided a supporting leg H0 adapted to engage, when rotateddownwardly, a base plate III thereby to limit the rotative movement ofthe member I01 in a clockwise direction. Its opposite relative movementis limited by means of a projection H2 adapted to coact with apush-button II 3 of a micro-switch I I4, the purpose of which will bepresently explained.

There is another micro-switch H5 mounted upon a transverse support H6 inthe frame of the machine, the actuating button II! of which is adaptedto be engaged by an adjustable mechanical contact member H8 mounted uponthe vertically reciprocating portion 3| of the crosshead. Thismicro-switch H5 is generally open and is closed when the contact memberII8 reaches approximately its lowermost position, to complete thecircuit through the starting switch controlling the solenoid 80 and,thru it, the operation of the feed rolls.

Assuming the parts to be substantially in the position shown in Figure1, but with the stop lip 60 raised and in the path of travel of thestock 52, the latter is inserted laterally and towards the left betweenthe spaced apart feed rollers 53 and 54 until it reaches this upwardlyextending stop lip 60, whereupon its inward movement is arrested. Atthis time, the motor 22 has already been independently started and themain shaft 23 is being rotated through the belt drive as shown in Figure2a. A foot pedal I (Figure 2a) is now depressed and motion istransmitted through turnbuckle I2I supported on pivoted arm I22 to throwin clutch 25 and start the reciprocation of the crosshead.

The stop lip 60 is provided with suitable adjusting means I23 where itmay be moved relatively tangentially, to the right or left of the axisof the shaft I08 (Figure 12) about which it turns, thereby toaccommodate the operation of the machine to the length of punchings tobe made from the stock and the time at which the end of the strip 52 isto reach the punch 50 for the first operation.

I-Iaving'thus described the various parts, we may consider theircombined action. With the crosshead 35 already in motion and with thestock 52 already in position between the feed rolls and against the stop60, when it is desired to start production, the starting button I24, ispressed.

Then the next contact between H8 and H5 closes the latter micro-switch,energizes the solenoid 80, draws the feed rolls 53, 54, together, andsimultaneously withdraws stop 60 from the path of the stock 52. Thisoccurs just as the crosshead and the punch reach the bottom of thestarting stroke. At this point, the brak 96 is off because point 82 haspassed its extreme right hand position. Also, as stop 00 was withdrawn,part H2 closed micro-switch H4 and the circuit for continuous operationof the feed rolls, which will then continue in operation (by meansdescribed later) until the operator shall press the stop button.

It is to be noted, here, that the start button may be pressed at anytime but the feed mechanism will not be started until the contact H8closes the micro-switch H5 and this always will occur at exactly thepredetermined and correct feed starting time which feature is novel andnot to be found on other presses of this character.

Figure 13 is a diagrammatic view showing the relative timing of movementof the various parts and work stock during the operation of the machineand, as herein shown, the vertical line A indicates graphically thestroke of the vertically reciprocating portion 3| while the circle Bindicates the travel or movement of the part 35 of the crosshead. Duringthis movement of the two parts 3| and 35, the punching operation occursat substantially the bottom of the circle B, or in the 15 to right ofline A, i. e. the right half of arc C, and the 30 subtended by the are Cindicates that portion of the stroke during which the punch operatesupon and withdraws from the work stock. It is also approximately thepart of the circle in which the starting takes place when the solenoid,micro-switches, feed rolls, and part 60 all function. The arc D,approximately indicates that portion of the operation during which thefeed stroke may start and take place. If, for example, the feed of thework 52 is stopped at the end of 15 as at F, an additional fifty percent more stroke is permitted within which to further feed the stock. Inother words, the stock 52 may be stopped, even with a long pilot, at anypoint within 50 as indicated by the are E.

It will thus be seen that the present device permits the starter buttonto be pressed at any time or point in the cycle of the press, yet thefeeding of the stock will not be started until its proper predeterminedtime, namely, at the beginning of the are C. Simultaneously with this,the linkage between stud 86 and the brake 96 engaging the work stock 52at the extreme right of the machine (Figure 1) will have caused thisbrake to release. The movement of the solenoid 80, however, in movingthe rod 05 towards the right causes the adjustable stop I05 to engagethe upper end of the lever I 03 and swing the same relatively clockwiseor toward the right thus causing the lower end of the'lever I03 toengage the afi al r stud and roller I56 and turn the square member ID!upon its; axis IIlB- thereby to bring the stop lip 60 downwardly out ofthe path of travel of the work stock and hold it there until the feed isstopped. As the square member It! assumes the position shown in Figure lthe lug I I2 carried thereby engages the actuating button H3 of themicro-switch H4 thus causing a shorting out of micro-switch H5 andcompleting the circuit to hold the solenoid armature downwardly with'thefeed rollers 53 and 54 in operative engagement until released by thestop button.

In other words, the micro-switch H5 is only used for feed startingpurposes, that is, to complete the circuit after the starting buttonI24. is actuated, thereby to insure initial feeding of the stock 52 tothe punch 50 at the proper time in the sequence of the other operations.

It is thus seen that a series of properly timed and coordinated actionsoccur and, while apparently instantaneous in operation, neverthelesseach function has its proper place in a sequence to effect properlytimed starting of the feeder. The sequence begins with pressing of thestarter button and includes closing of micro-switch H5, energizingsolenoid 80, a drawing together and subsequent engagement of the feedingrollers 53-54 with the stock, the release of the brake 96 and withdrawalof the stop lip 60 whereby the strip, or stock is subsequently fedtoward the punch 55, intermittently until the entire strip has beenacted upon and the final end discharged through the exit feed rollers56-57.

Die bed adjustment As will, of course, be understood by those familiarwith the subject, it is quite important that there be adjustment made inthe relative position of the die bed 55 depending upon the thickness ofthe stock being worked and of the die and its supports. This will alsonecessitate an adjustment of the feed rollers 5354 not only as to theirrelative height with respect to the die bed 55 but also their separationrelative to each other.

Thus it is necessary to first position the die bed 55 Figure la, bymoving the same vertically up or down with respect to the end of thestroke of the die punch and in accordance with the thickness of'thestock upon such bed. This may be accomplished as follows: The lower partof the casing is provided with two inwardly extending arms I26 havingvertical bores or sleeves acting as bearings for supporting rods I21.The lower ends of these rods are threaded and act as jack screws I23, asthreaded sleeves I30 at their lower ends are turned. The upper ends ofthese rods support the die bed 55 as clearly shown in Figure la. Thesleeves I31! surrounding the threaded lower portions I28 of these jacksare provided with worm wheels I3I which are adapted to be engaged byworms I32 and mounted upon adjacent ends of a transversely extendingshaft I33 mounted in suitable bearings I34 in the side walls of thecasing 20, One end of this shaft, preferably the left as shown in Figure 1a for convenience of operation, is provided with an actuatinghandle I35.

This gearing is suitably calibrated whereby one revolution of theoperating handle I35 will raise or lower the die bed 55 a predeterminedand known amount. It has been. found by experience that one-fifth of aturn of the handle to raise the die bed .002" is a convenient ratio ofoperation.

When the die bed55 is raised or lowered, suitable adjustment in therelative height of the feed roller frame shown in Figure 4, with respectto the die 5I- must also be made. the point of tangency of the lowerroller 54 should be exactly level with the top surface of the die. Thisadjustment is preferably accomplished by loosening the two nuts I31 andmoving them to raise or lower the lower feed roll 54 until its topsurface is in horizontal alignment with the top of the die 5|. Then thenut I36 passing through a fixed portion of the frame I40, (see left handside of Figure 1a,, the right; hand plate being provided with similarmembers, not shown) is loosened and the housing in whichis formed a slotMI is raised or lowered in order to bring the top roller 53 and thelower feed roller 54 into vertical alignment; the lower feed rollerhaving been adjusted exactly to the level of the die 5!. This operationis performed on both adjustments, at the right and left sides of thecasing.

A universal connection I42 in roller drive shaft I43 permits subsequentdrive without binding.

A further adjustment of the feed rollers towards and fromeachother, attheir point of tangency, to accommodate the thickness of the stock,

is performed by means of the adjusting nuts I44 at the right end of linkor rod 65 between which nuts the upper end 61 of the bellcrank leverfunctions.

Another adjustment necessary is that for con-- trolling the amount offeed of the stock at each, punching operation. As previously stated, the

exterior surfaces" of the feed rollers 53-54 are segmental, (Figures 5and 6) that is, one-half of each roller, for example, is of less radiusthan the other half and by rotating these feed roller surfacesrelativeto each other, the segment, of larger diameter, can bepositioned, to overlapthe m n o h o h r r011, b an s re amcurt, from asmall fraction to the entire half-circumference.

By referring to Figure 3 it will be seen that to accomplish thislastadjustment it is only. nee.-

essary to loosen nut I56 which, thre adedly en gages the shaft I5Icarrying this feed roller 53 thereby allowing a compression spring I52,acting againsta fixed collar; I53, to force a, cone I54 relativelytowards the left, as, shownin this, view, whereupon, the surface oftheupper feed roller.

53 may be rotated relative I10. that of the lower feed roller 54, asdesired, to properly proportion.

or a just the extent of en a m nt of the. fee su faces. of a r diam t rwith the sto k.

As stated these feed rollers 53 and 54 are about which a chain (notshown) passes to. a

corresponding sprocket upon the lower feed roll. er 51 at the oppositeor left side of themachine shown in Figure 1.

both sets of feed rollers through the above described gears, chain I56and. sprocket I62, in proper synchronism, when the clutch 25 is thrownin.

In other words,

Thus the power obtained from the main power shaft 23 of the pressdrives- V Lubricating system The various important moving parts of thepress herein disclosed are preferably lubricated by means of a forcedfeed lubricating system such as shown in Figure 8. In the lower rearinterior of the casing 20 a suitable reservoir I63 is provided' as wellas a suitable pump I64, preferably driven by an independent; motor I65,thereby to provide a continuous stream of oil flowing over the variousmoving parts whether temporarily at rest or in rapid operation. Leadingfrom the outgo side of pump I64 is a relatively large pipe I66 extendingupwardly at the rear of the machine and thence forwardly across the topat I61 where it is provided with two branches I60I'I0 going to theopposite sides as well as towards the front of the press. The ends ofthese forwardly extending branches I68-II0 then pass downwardly at IIII'I2 to supply respectively a plurality of smaller branche I'I3-II4leading to the upper and lower parts of the vertical gibs 30 as well asto the upper central part of the transverse gibs 36 for the innercrosshead. By reference to Figures 10 and 11 these branch pipesterminate adjacent the groove I15 thereby to maintain the same properlylubricated at all times. The lower gibs of the horizontal crosshead 35are preferably entirely immersed in a suitable tank or pan I'I6 Figure 8adapted to catch the drip from the variou gibs thus insuring especiallya proper lubrication of the lower guides for the horizontal slides. Fromthis tank I16 the oil drains back through pipe I'II into the reservoirI63 in the bottom of the casing. The feed roller bearings may beindependently lubricated in any desired manner.

Single operation It frequently becomes desirable under certaincircumstances to perform a single punch or die operation upon a piece ofmetal at some particular point and the present machine is readilyadaptable to such functions and operations, since it is only necessaryto remove the feed rolls and plug I80 and use the foot pedal I20 tocontrol the machine stroke by stroke.

Circuits In Figure 7 there is shown a wiring diagram, in simplified formand with parts similarly identified by reference numbers. The parts arepositioned for single operation but on inserting the plug I80 themachine becomes ready for continuous high-speed. operation. Assume theplug I80 is connected, then the course of the current in the maincontrol circuit is from L, through M to R and on to I24, normally openstarting switch,

to H another normally open switch, thru I82, a normally closed stopswitch, to L2.

For continuous operation, I80 is connected at R. and the micro switchH4, normally open, is mechanically linked to the solenoid 80.

As previously described, micro switch H5. is closed, by H8, (Figure 1),at the bottom of each stroke of the punch. Therefore, when the startingswitch I24 is closed by the operator of the press, the main circuit iscompleted. Current then passing thru MC, closes switch MS and energizesthe solenoid, 60, which operates to close I I4.

Then, switch I I5 is short circuited and itssubsequent repeated openingand closing does not interrupt the flow of current thru the solenoidwhich, therefore, keeps switch II4 closed and cffects continuous feedingof the press by the feed rolls in the manner previously described.

The new, short circuit is from LI thru MC and and MS to R and thru H4and I82 to L2. To stop the crosshead the foot pedal I20 must be pressedto disengage the clutch 25. To stop the flywheel and clutch the mainmotor control switch must be opened.

The construction and operation of the complete machine is clear from theabove explanation and accompanying drawings. It will be seen that themachine is of practical construction and substantially fool proof andautomatic in its operation. It will operate at extremely high speed byreason of the novel construction of the actuating means and by reason ofthe high speed impact blow on the punch head driving the metal out ofthe work strip without necessitating the entry of the punch or tool intothe die. Thus the life of the machine and particularly the die and punchis very materially increased. The machine is well adapted to accomplishamong others, all of the objects and advantages herein set forth.

Without further analysis the foregoing will so fully reveal the gist ofthis invention that others can, by applying current knowledge, readilyadapt it for various applications without omitting certain featuresthat, from the standpoint of the prior art, fairly constitute essentialcharacteristics of the generic or specific aspects of the invention, andthereforesuch adaptations should and are intended to be comprehendedwithin the meaning and range of equivalency of the following claims.

I claim: a

1. In a high speed punch press of the character described, incombination, a punch and die, means for actuating said punch including apart traveling throughout its working stroke at speeds varying from zeroto maximum and back to zero,-

means for causing the punch, when near the end of the stroke of saidpart, to be impacted, when already in contact with-the work, at a speedcorresponding to the maximum speed attained by said part.

2. In a high speed press of the character described, in combination, apunch and die,means for actuating said punchincluding a part havingworking speed varying from zero to maximum and back to zero, and amember for causing the punch after first being pressed against the workby and when said part is near the end of its stroke, to be impacted, anddriven through the work ata speed corresponding to the maximum speedattained by said part, said member and part moving at right angles toeach other and having a sliding connection to engage the punch andconvert its movement into movement at substantially right angles to themovement of the part.

3. In a high speed press of the character described, in combination, apunch and a die movable relative to each other, means for actuating saidpunch including a movable part having a working speed varying from zeroto maximum and thence to zero, and means for causing the tool, when nearthe end of the stroke of said part and already pressing upon the work,to be driven through the work at a speed corresponding to the maximumspeed attained by said part throughout said stroke, said last mentionedmeans including a second movable part reciprocating at right angles tosaid first movable part with its movement of highest speed being at themoment of rest of the first part. I

4. In a high speed press of the character described, the combination ofa punch and a die, means for actuating said punch including two partsmoving throughout their working strokes at speeds varying from zero tomaximum and back to zero, for causing the punch, when near the end ofthe stroke of one part, to first press and then, by impact of the otherpart to act upon the work at a speed corresponding to the maximum speedsattained by the parts.

5. In a high speed press of the character described, the combination ofa tool and a die, means for actuating said tool, including two partsmoving throughout their working strokes at speeds varying from zero tomaximum and back to zero, for causing the tool, when near the end of thestroke of one part and in substantial engagement with the work, to beimpacted by the other part while moving at a speed corresponding to themaximum speed attained by either part throughout its stroke, saidmovements of the two parts being substantially at right angles, with themoment of highest speed of one being at the moment of rest of the otherand being the moment of impact with the tool.

6. In a high speed punch press machine having a die and punch, incombination, means for reciprocating one of said parts, including adrive shaft, eccentric means driven thereby, and two reciprooablemembers one having an inclined impact surface and both relatively andsimultaneously movable at substantially right angles under the action ofsaid eccentric means, whereby one member is brought substantially to theend of the stroke movement of that member to carry the punchsubstantially into contact with the work at the same moment when theother reciprocating part is brought substantially to its highest speedto impact the punch and drive it through the work.

'7. A machine according to claim 6 in which the impacting surfaces areoppositely curved.

8. A machine according to claim 6 in which the head of the punch isrounded thereby better to receive the impacting blow struck by themember engaging the same.

9. A machine according to claim 6, in which the reciprocating membersmove one in a horizontal and the other in a vertical path.

10. A machine according to claim 6, in which,

the reciprocating part is travelling at substantially its highest speedwhen the other member is at substantially the end of its reciprocatingmovement.

11. A machine according to claim 6, in which the movement of that one ofsaid members ending its stroke is in the direction of movement of thepunch and in which the movement of the other member, causes the largerpart of the actual punching.

12. A machine according to claim 6, in which the movement of that one ofsaid members bringing the punch into engagement with the work is in thedirection of movement of the punch.

13. In a high speed punch machine having a stationary die and reciprocalpunch, in combination, means for reciprocating said punch including adrive shaft, eccentric means driven thereby, and two reciprocablecrosshead members relatively movable at substantially right angles toeach other under the action of said eccentric means, one of said membersbeing partially carried and driven by the other member and havingmovements in a vertical direction, the ends of the vertical movementbeing at the momentsiof highest speed of. the relatively horizontallymovablecarrier member which engages and actuates th penetration of thepunch by impact. v

14 A machine as set forth in claim 13 in which thetop of the punch isrounded to more effectively receive the impact of the horizontallymovable member.

15. A machine according to claim 13, having feeding means for moving aWork piece with respect to the punch, intermittently, said feeding meansincluding two sets of feed rollers at'opposite sides of the punch andmeans for adjusting circumierentialiy the surface only of one feedroller relative to the other to any desired degree thereby to controlthe feed of the work strip one of said feed rollers being hollow andhaving a cone surface at one end and a cone member coincident with theaxis of the roller to hold the roller in adjusted position.

16. In a high speed press machine, in combina tion, a punch and die,means for actuating said punch including a two part crosshead, each ofthe parts of which is reciprocated in a relatively diiTerent directionand phase whereby one brings the punch substantially into contact withthe work in time "to enable the other crosshead part to actuate thepunch, by impact, at the moment of the latter parts highest speed.

17; A machine according to claim 16 in which the contacting surfaces ofsaid crosshead part and punch are curved towards each other to emphasizethe impact.

18. A machine according to claim 16 including a control circuit, andmeans for converting the machine from continuous to single operation andvice versa as desired.

19. A machine according to claim 16, including means for feeding a workstrip to the punch, means for braking and releasing the work feed, andmeans for determining the moment of release with respect to the positionof the punch.

20. A machine according to claim 16 including of different radiicoacting to efiect intermittent feed and means for adjusting thesurfaces of one radius on one roller with respect to the surfaces of theother roller to regulate the extent of feed to any desired degree, oneof said rollers being hollow and having a cone surface at one end and acone member coincident with the axis of the roller to hold the roller inadjusted position.

21. A machine according to claim 16 including a pair of feed rollers oneof which is hollow, means for circumferentially adjusting said hollowroller with respect to the other and means for positively setting andholding said hollow roller in position with respect to the other saidlast means including a cone surface at one end of said hollow roller anda cone member coincident with the axis of the roller adapted to hold theroller in adjusted position.

22. A machine according to claim 16 including a work stock feed brake,and means connecting one of the parts of the crosshead with the brake torelease said brake with respect to the movement of said part.

23. A machine according to claim 16 including a work stock feed brake,and means connecting one of the parts of the crosshead with the brake torelease said brake with respect to the movement of said part, and meansfor adjusting the time of release.

24. In a high speed machine of the character described, in combination,a tool and die, means for actuating said tool including a part travelingthroughout its working stroke at speeds varying from zero to maximum andthence to zero to bring the tool substantially into contact with thework, reciprocating means for causing the tool, when near the end of thestroke of said first means, to be driven through the work by impact at aspeed corresponding to the maximum speed attained by said meansthroughout its stroke, said last-mentioned means traveling atsubstantially right angles to said first-mentioned means and themovement of the tool.

25. A machine according to claim 24 including a means for positioningthe machine stock at the beginning of the operation with relation to themovement of the tool whereby on release the work stock will be fed tothe tool and give a perfect blank at the end of the first work stroke.

26. A machine according to claim 25 including a means for positioningthe work strip at the beginning of the operation with relation to themovement of the tool, a motor drive and circuit with contacts in whichthe contacts are closed as a work strip is fed into engagement with thecontact to start the motor and insure a perfect blank on the firstcomplete down stroke of the tool.

27. In a high speed press of the character described, in combination avertically moving punch, a horizontally reciprocating crosshead havingan inclined part to impact the punch, a motor for the press, a controlcircuit, a pair of feed rollers having segmental surfaces of differentradii coactnig to effect intermittent feed, and means for adjusting thesurfaces of one radius on one roller with respect to the surface of theother roller to regulate the extent-of feed to any desired degree.

28. In a high speed press of the character described, in combination avertically moving punch, a horizontally reciprocating crosshead havingan inclined part to impact the punch, a motor for the press, a controlcircuit, a pair of feed rollers having segmental surfaces of dilferentradii, means for adjusting surfaces of one radius with respect to theother to regulate the extent of feed, means for supporting the die, andmeans for adjusting the die towards and from the punch, said lastmentioned means including an operating handle one revolution of which isknown to move the die support a predetermined known amount.

29. In a high speed press of the character described, in combination apunch, a reciprocating crosshead to impact the punch while moving at itshighest speed and in a direction at substantially right angles to themovement of the punch, a motor for the press, a control circuit, a workstrip, a feed brake, and means connecting one of the parts of thecrosshead with the brake to release said brake with respect to themovement of said part.

30. In a high speed press of the character described, in combination apunch, a reciprocating crosshead to impact the punch while moving at itshighest speed and in a direction at substantially right angles to themovement of the punch, a motor for the press, a control circuit, a workstrip, a feed brake, and means connecting one of the parts of thecrosshead with the brake to release said brake with respect to themovement of said part, and means for adjusting the time of release.

GEORGE B. SCHEFFEY.

